Planetary gearset

ABSTRACT

A planetary gearset provided with a sun gear, a ring gear, and a carrier that rotatably retains a plurality of pinion gears arranged between the sun gear and the ring gear as elements, in which one of the elements is made a fixed element and one of the other elements is made a rotating element, and which transmits torque between that rotating element and an external member provided in a location eccentric with respect to that rotating member. The planetary gearset is constructed such that the fixed element is movably retained in the direction of a load from the transmission of torque between the rotating element and the external member, and the load from the transmission of torque between the rotating element and the external member is received by a fixed portion that rotatably retains that rotating element.

BACKGROUND OF THE INVENTION

1. Field of the Invention

The invention relates to a planetary gearset, the main components ofwhich are a sun gear, a ring gear, and a carrier that retains piniongears (planet gears) arranged between the sun gear and the ring gear.

2. Description of the Related Art

Typically, a planetary gearset is a device in which a sun gear, which isa gear with external teeth, and a ring gear, which is a gear withinternal teeth, are arranged on the same axis, with pinion gearsarranged between the sun gear and the ring gear, which are retained bythe carrier so as to be able to rotate and revolve. With respect tothese pinion gears, a device provided with pinion gears that engage withboth the sun gear and the ring gear at the same time has been known. Inaddition, a device provided with a first pinion gear that engages withthe sun gear, and a second pinion gear that engages with the firstpinion gear and the ring gear has also been known.

The former planetary gearset is commonly referred to as a single piniontype planetary gearset, while the latter planetary gearset is commonlyreferred to as a double pinion type planetary gearset. Moreover, aRavigneaux type planetary gearset, in which a single pinion typeplanetary gearset is integrally combined with a double pinion typeplanetary gearset, has also generally been known.

A planetary gearset of this type of configuration has three mainelements, which are a sun gear, a ring gear, and a carrier. Theplanetary gearset functions as a decelerating device, an acceleratingdevice, and a reversing device and the like by making one of thoseelements an input element, another one an output element, and anotherone a fixed element. Coupling together any two of the elementsintegrates the entire planetary gearset.

Regardless of the mode of use, the pinion gears become the mediumthrough which torque is transmitted between the sun gear and the ringgear. Accordingly, the more pinion gears there are, the more torque thatcan be transmitted between the sun gear and the ring gear. Therefore,the invention disclosed in Japanese Patent Laid-Open Publication No.4-175542, for example, increases the number of pinion gears that can beretained by the carrier by changing the structure of the carrier.

In this publication it is disclosed that, assuming that the torqueapplied to each of the plurality of pinion gears is equal, when fiveinstead of four pinion gears are provided, the torque able to betransmitted increases by 1.25 times. Depending on the mode of use of theplanetary gearset, however, a large load may end up being applied to aspecific pinion gear, thereby leading to a decrease in strength anddurability of the planetary gearset.

More specifically, FIGS. 33 and 34 show an example of two pinion gears 3arranged between a sun gear 1 and a ring gear 2, with a carrier 4 thatretains those pinion gears 3 fixed by splines 6 to a casing 5. Inaddition, a counter gear 8 is engaged with external teeth 7 formed on anouter peripheral face of the ring gear 2. In addition, the ring gear 2is supported by the casing 5 via a bearing 9 fitted at the outerperiphery of the ring gear 2. In this kind of mode of use, a load F fromthe transmission of torque acts between the ring gear 2 and the countergear 8. In FIG. 33, the pressure angle is ignored, so the load F acts ina direction at a right angle to a virtual line connecting the center ofthe sun gear 1 with the center of the counter gear 8.

Meanwhile, with respect to the fact that there is an inevitable gap ebetween the casing 5 and the bearing 9 that supports the ring gear 2, acarrier 4 is fixed to the casing 5, so a reaction force against the loadF acts between the pinion gears 3, which are supported by the carrier 4,and the ring gear 2. Further, a load following the transmission oftorque acts on each of the pinion gears 3.

Accordingly, the relationship between forces f1 and f2 that act on thepinion gears 3 and the load F is as shown by the arrows in FIG. 33, withthe amount being:f1=(F/2)*{(R/r)+1}f2=(F/2)*{(R/r)−1},wherein the radii r and R of the contact point between the pinion gears3 and the ring gear 2 is the radius of the location upon which the loadF acts.

The pinion gears 3 also mesh with the sun gear 1 and transmit the torquethereto, so the bearings of the pinion gears 3 receive a radial loadthat is two times that of each of the forces f1 and f2.

In this way, the force f1 acting on the pinion gear 3 that is closest tothe contact point between the ring gear 2 and the counter gear 8 islarger than the force f2 acting on the other pinion gear 3. As a result,the strength or durability of the pinion gear 3 upon which the load islargest restricts the strength or durability of the overall planetarygearset.

This is true even when another element is fixed instead of the carrier 4and torque is transmitted between another element that is not fixed andthe rotating member outside of the planetary gearset. That is, therelated art does not take into consideration the effect of the loadgenerated by the transmission of torque between the rotating memberoutside of the planetary gearset and the planetary gearset. As a result,with the related art, the strength and durability of the overallplanetary gearset is restricted by the strength and durability of aspecific member.

Further, because the sun gear and the ring gear in the type of planetarygearset described above are rotatably arranged on the same axis, thebearings retaining these gears can be fixed on the outer periphery of apredetermined shaft or fixedly fitted to a boss portion that isintegrated with the casing. As a result, those bearings can belubricated relatively easily by supplying lubricating oil via the shaftor the boss portion.

On the other hand, because the pinion gears have a comparatively smallerdiameter than the sun gear and the ring gear and transmit torque betweenthose two gears, the pinion gears rotate quickly and receive a largeload. In addition, these pinion gears are fitted via bearings to pinionpins attached to the carrier, so those bearings are separated from thebearing that supports the sun gear and the bearing that supports thering gear.

In this way, there are times when the load and speed conditions on thebearings that support the pinion gears are severe, so it is importantthat they be sufficiently lubricated. In this case, the bearings of thepinion gears can be lubricated by supplying lubricating oil to therotational center of the carrier when the carrier is rotated. Thislubricating oil then reaches the bearings of the pinion gears bycentrifugal force from the rotation of the carrier, and lubricates them.However, in the planetary gearset, one of the rotating elements is oftenused as a fixed element. When the carrier is made that fixed element,the centrifugal force used in the lubrication of the pinion gearsretained by that carrier is no longer available.

Here, Japanese Patent Laid-Open Publication No. 2001-227625 discloses adevice in which a lubricating oil path forming member is fixed to oneside of a carrier that is fixed to a case, the device supplyinglubricating oil to the carrier via an oil path formed in the case andthe lubricating oil path forming member. According to this construction,lubricating oil can be supplied to the carrier (or more correctly, tothe pinion bearings) arranged between the rotational axis of theplanetary gearset and an inner peripheral face of the case.

With the device disclosed in the aforementioned publication, lubricatingoil is supplied to each of the pinion bearings by running naturally downthe lubricating oil path. With respect to the lubricating oil formed inthe vertical direction, however, oil holes leading the lubricating oilto the pinion bearings are formed orthogonal to the lubricating oilpath, which makes it difficult to lead the lubricating oil runningdownward into the oil holes. As a result, the lubricating oil that hasrun down ends up collecting on the lower side. The lubricating oilcollects until it reaches the height of the open edge of the oil holes,after which it enters the oil holes and is supplied to the pinionbearings.

Therefore, because the carrier does not revolve, the pinion bearing thatis stopped on the upper side is not lubricated until the lubricating oilrises, which takes a long time. Further, when only a small amount of thelubricating oil runs down, a sufficient amount of lubricating oil doesnot collect so the level thereof does not rise, which may result in theproblem of lubricating oil not being able to be supplied to the pinionbearing on the upper side.

Furthermore, a lubrication system is generally known that supplieslubricating oil to portions where there is friction and portions whereheat is generated in a planetary gearset or the like such as thatdescribed above. Also, even in a typical gear mechanism that is not aplanetary gearset, a lubrication system is widely known that lubricatesand cools by kicking up lubricating oil to portions where there isfriction and portions where heat is generated. One example of such adevice is disclosed in Japanese Patent Laid-Open Publication No.7-217725. In a differential gear disclosed in this publication, a driveshaft and a ring gear are rotatably provided in a differential carrier.Further, a hypoid gear formed on the drive shaft is engaged with thering gear, and the drive shaft is supported by a bearing. Moreover, alubricating oil sump is provided in the differential carrier, and aportion of the ring gear is submersed in the lubricating oil sump. Also,an oil reservoir with an inflow opening is provided inside thedifferential carrier above the drive shaft. An outflow opening is alsoformed above the drive shaft in the oil reservoir.

In the lubrication system of the aforementioned publication, when torquefrom the drive shaft is transmitted to the ring gear, the ring gearrotates and kicks up lubricating oil from the lubricating oil sump. Whenthis happens, some of the lubricating oil adhered to the ring gear isthrown by centrifugal force in a direction tangential to the ring gear.This lubricating oil passes through the inflow opening and runs into theoil reservoir, after which it naturally drips down from the outflowopening to lubricate and cool the bearings.

In the lubrication system described in this publication, however, thelubricating oil is supplied to the oil reservoir in only one transferstep, being the transfer of the lubricating oil in the lubricating oilsump by the rotation of the ring gear. Therefore, when the oil reservoirand the ring gear are separated by a large distance, there may be adecrease in the amount of lubricating oil supplied to the oil reservoir.More specifically, when the rotation speed of the ring gear drops belowa predetermined rotation speed, the centrifugal force, which is used tothrow the lubricating oil, is weak, making the aforementioned problemeven more pronounced. As a result, the degree of freedom of the layoutof the oil reservoir and the ring gear is reduced. In order to solve theforegoing problems, the amount of lubricating oil kicked up by therotation of the ring gear can be increased by increasing the surfacearea of the ring gear that is submersed in the lubricating oil sump.However, this creates another problem of increased power loss during therotation of the ring gear due to the shearing resistance of thelubricating oil.

SUMMARY OF THE INVENTION

In view of the foregoing technical problems, it is one object theinvention to provide a planetary gearset able to improve characteristicssuch as overall strength and durability by suppressing a load fromtorque transmission between an external member and the planetary gearsetfrom acting more on one member (i.e., on a specific member) than onanother.

Also, it is a second object of the invention to provide a lubricationsystem capable of supplying a sufficient amount of lubricating oil to apinion bearing in a planetary gearset in which a carrier is fixed.

Still further, it is a third object of the invention to provide alubrication system capable of suppressing a decrease in an amount oflubricating oil supplied to an oil reservoir, even if a rotating bodyand the oil reservoir are separated by a large distance; capable ofsupplying the lubricating oil to the oil reservoir that is in a locationseparated from a first rotating body, regardless of the rotation speedof that first rotating body; suppressing an increase in power loss ofthe first rotating body; and suppressing a decrease in a degree offreedom of a layout of a portion requiring lubrication and the firstrotating body.

In order to achieve the first object of the invention, according to afirst aspect of the invention, a fixed element is able to move in aradial direction from torque transmitted between an external rotatingmember and a rotating element other than that fixed element when torqueis transmitted between that external rotating member and the otherrotating element, and that other rotating element receives the radialload. More specifically, according to a first exemplary embodiment ofthe invention, a planetary gearset is provided with a sun gear, a ringgear, and a carrier that rotatably retains a plurality of pinion gearsarranged between the sun gear and the ring gear, as elements. In thisplanetary gearset, one of the elements is made a fixed element whileanother is made a rotating element. This planetary gearset transmitstorque between that rotating element and an external member that isprovided in a location eccentric with respect to that rotating element.The fixed element is retained so as to be able to move in the directionof the load from the torque transmitted between the rotating element andthe external member. A fixed portion that rotatably retains the rotatingelement receives the load from the torque transmitted between therotating element and the external member.

Therefore, according to the first aspect of the invention, the load fromthe transmission of torque between the rotating element and the externalmember is transmitted to the fixed element via the pinion gear. As aresult, the fixed element moves from the load. That is, the fixedelement and the pinion gear do not support the load. When the fixedelement moves, the rotating element moves to close a gap between it andthe fixed portion, such that the fixed portion receives the load.Accordingly, although the load from the transmission of torque betweenthe sun gear and the ring gear acts on the pinion gears, that load isnot applied unevenly among the pinion gears. As a result,characteristics such as strength and durability of the overall planetarygearset are not restricted by the strength and durability of a specificpinion gear.

Also with the planetary gearset according to the first aspect of theinvention, it is possible to retain the fixed element on the fixedportion via an elastic member. As a result, the fixed element is able tomove, and the elastic member acts as an absorber so noise and vibrationare able to be minimized or eliminated.

Also, with the planetary gearset according to the first aspect of theinvention, it is also possible to make the fixed element the carrier andthe rotating element the ring gear. Accordingly, torque is transmittedbetween the ring gear and the external member, with the carrier movingby the load from that transmission in the direction of that load. As aresult, the gap between the ring gear and the fixed portion closes andthe load is supported by the fixed portion through the ring gear suchthat a case in which a larger load is applied to one of the pinion gearsretained by the carrier than another is suppressed. Therefore, it ispossible to improve the characteristics such as strength and durabilityof the planetary gearset on the whole.

Meanwhile, in a planetary gearset according to a second aspect of theinvention, a plurality of pinion gears are arranged in thecircumferential direction between a sun gear and a ring gear which areon the same rotational axis. These pinion gears are rotatably mounted toa carrier which is fixed so as not to rotate, and torque is transmittedbetween the sun gear or the ring gear and an external member which iseccentric with respect to the sun gear and ring gear. In addition, thesepinion gears are arranged away, in the circumferential direction, fromthe location at which torque is transmitted (hereinafter, referred to as“torque transmitting point”) between the sun gear or the ring gear andthe external member.

Accordingly, because the carrier does not rotate, the load from thetransmission of torque between the sun gear or the ring gear and theexternal member acts on the pinion gears retained by the carrier.Because the pinion gears are arranged away, in the circumferentialdirection, from the torque transmitting point between the sun gear orthe ring gear and the external member, the load tends to be distributedbetween the plurality of pinion gears. As a result, the loadconcentrates less on any one pinion gear, thereby improving thecharacteristics such as strength and durability of the planetary gearsetas a whole.

Further, in the planetary gearset according to the second aspect of theinvention, the pinion gears may also be arranged such that the torquetransmitting point lies between two of the pinion gears.

Accordingly because there are two pinion gears on which the load tendsto concentrate, the load on these pinion gears is distributed such thatthe load on any one of the two pinion gears becomes relatively light. Asa result, the characteristics such as strength and durability of theplanetary gearset as a whole are able to be improved.

In a planetary gearset according to a third aspect of the invention, aplurality of pinion gears are arranged in the circumferential directionbetween a sun gear and a ring gear which are arranged on the samerotational axis. These pinion gears are rotatably mounted to a carrierwhich is fixed so as not to rotate, and torque is transmitted betweenthe sun gear or the ring gear and an external member which is eccentricwith respect to the sun gear and ring gear. In addition, more of thepinion gears are arranged in an area near, in the circumferentialdirection, the torque transmitting point where torque is transmittedbetween the sun gear or the ring gear and the external member than in anarea away from that torque transmitting point.

Accordingly, because more of the pinion gears are arranged in an areanear, in the circumferential direction, the torque transmitting pointwhere torque is transmitted between the sun gear or the ring gear andthe external member, and because the carrier is fixed so as not torotate, the relative position of the torque transmitting point and thepinion gears is maintained. As a result, an uneven load from the torquetransmitted between the sun gear or the ring gear and the externalmember is distributed between more pinion gears, such that the loadacting on any one pinion gear is relatively light. As a result, thecharacteristics such as strength and durability of the planetary gearsetas a whole are able to be improved.

In order to achieve the second object of this invention, in theplanetary gearset according to any one of the first through thirdaspects of the invention, an oil sump that collects some of thelubricating oil that naturally runs down and which then supplies thatlubricating oil to pinion bearings is provided midway in an oil pathwhich leads that lubricating oil. More specifically, in a planetary gearlubrication system of a planetary gearset, a plurality of pinion gearsis arranged between the sun gear and the ring gear, which are on thesame rotational axis. These pinion gears are rotatably retained viabearings by pinion pins mounted to the carrier which is constantlyfixed. A passage that leads the lubricating oil that runs down fromabove is formed that connects the axial ends of the pinions pins fromthe axial ends of the upper pinion pins to the axial ends of the lowerpinion pins in that order. Furthermore, an oil sump is formed at alocation corresponding to the axial end of at least one of the pinionpins. This oil sump collects the lubricating oil that runs down into it,and is intercommunicated with the at least one of the pinion pins.

Therefore, in the planetary gearset according to any one of the firstthrough third aspects of the invention, as the lubricating oil runs downthe oil path vertically connecting the axial ends of the pinion pinsretained by the fixed carrier, it runs into the oil sump formed in amiddle portion and collects here. Communication between this oil sumpand the bearings fitted to the pinion pins enables the lubricating oilto be supplied to the pinion bearings from this oil sump. That is, evenwith a pinion bearing that is positioned relatively high, thelubricating oil collects in the oil sump provided in a relatively highlocation that corresponds to that pinion bearing and is supplied to thepinion bearing from this oil sump. As a result, the lubricating oil issupplied to the pinion bearing that is positioned relatively high so asto lubricate it soon after the lubricating oil starts to be supplied tothe oil path.

Also in order to achieve the second object of the invention, in theplanetary gearset according to any one of the first through thirdaspects of the invention, a plurality of pinion gears is arrangedbetween the sun gear and the ring gear, which are on the same rotationalaxis. These pinion gears are rotatably retained via bearings by pinionpins mounted to the carrier which is constantly fixed. Further, aplanetary gear bearing lubrication system of the planetary gearset isprovided in which oil holes extending from the axial ends of thosepinion pins to the bearings are formed in the pinion pins. In thisplanetary gear bearing lubrication system, an oil path leadinglubricating oil that runs down from above is formed that connects theopen ends of the oil holes from the open ends of the upper oil holes tothe open ends of the lower oil holes in that order. Furthermore, an oilsump is formed at a location corresponding to the open end of at leastone of the pinion oil holes. This oil sump collects the lubricating oilthat runs down into it, and is intercommunicated with the at least oneof the pinion pins.

Therefore, in the planetary gearset according to any one of the firstthrough third aspects of the invention, an oil path which opens to oilholes formed in the pinion pins is formed in the vertical direction. Thelubricating oil is supplied to this oil path from above and runsdownward. As the lubricating oil runs down the oil path verticallyconnecting the axial ends of the pinion pins retained by the fixedcarrier, some of it runs into the oil sump formed in a middle portionand collects here. Because the oil holes open to this oil sump, thelubricating oil is able to be supplied to the pinion bearings throughthese holes from this oil sump. That is, even with a pinion bearing thatis positioned relatively high, the lubricating oil collects in the oilsump provided in a relatively high location that corresponds to thatpinion bearing, and is supplied to the pinion bearing from this oilsump. As a result, the lubricating oil is supplied to the pinion bearingthat provided in a relatively high position so as to lubricate it soonafter the lubricating oil starts to be supplied to the oil path.

In the planetary gearset according to any one of the first through thirdaspects of the invention, a plurality of the oil sumps may also beformed, and one of those oil sumps may be formed with a differentlubricating oil collecting capacity than the other oil sumps.

Accordingly, the speed with which the lubricating oil collects, and theamount of lubricating oil collected, differ depending on the shape ofthe oil sump. As a result, lubricating oil at a speed and of an amountin accordance with the shape of the oil sump may be supplied to thepinion bearings via the oil holes in the pinion pins that arrangedcorresponding to the oil sumps.

Furthermore, in order to achieve the third foregoing object of theinvention, in a planetary gearset according to any one of the firstthrough third aspects of the invention, a lubrication system thatsupplies a portion requiring lubrication with lubricating oiltransferred by rotation of a first rotating body, has a second rotatingbody which retains lubricating oil transferred by the rotation of thefirst rotating body to portions requiring lubrication, and transfersthat lubricating oil to the portion requiring lubrication by rotating.

According to this aspect, the lubricating oil is transferred in aplurality of steps, the first being the transfer of the lubricating oilby rotation of the first rotating body, and the second being thetransfer of the lubricating oil by rotation of the second rotating body.Accordingly, even if the first rotating body is separated from the oilreservoir, a reduction in the amount of lubricating oil supplied to theoil reservoir is able to be suppressed. In addition, the lubricating oilis able to be supplied to the oil reservoir even when that oil reservoiris separated from the first rotating body regardless of the rotationspeed of the first rotating body. Furthermore, it is possible tosuppress an increase in the surface area of the first rotating body thatis submersed in the lubricating oil.

BRIEF DESCRIPTION OF THE DRAWINGS

The foregoing and further objects, features and advantages of theinvention will become apparent from the following description ofpreferred embodiments with reference to the accompanying drawings,wherein like numerals are used to represent like elements and wherein:

FIG. 1 is a representative view illustrating the state of loads actingin a planetary gearset according to the invention;

FIG. 2 is another representative view illustrating the state of theacting loads;

FIG. 3 is a skeleton view showing one example of a planetary gearsetaccording to the invention;

FIG. 4 is a representative view showing another example of theinvention;

FIG. 5 is a line graph showing several examples of arrangements of aplurality of pinion gears and their load distribution ratios;

FIG. 6 is a front view showing one example of a shape of an oil path andan oil sump in a lubrication system according to the invention;

FIG. 7 is a cross-sectional view showing the lubrication system in FIG.6;

FIG. 8 is a front view showing an example of another shape of the oilpath and oil sumps according to the invention;

FIG. 9 is a cross-sectional view showing one example of a spacer thatcan be used in the invention;

FIG. 10 is a cross-sectional view showing one example of the inventionin which the spacer in FIG. 9 is used;

FIG. 11 is a cross-sectional view showing an example in which the spacerin FIG. 9 is attached to a partition portion;

FIG. 12 is a front view of one example of a spacer provided with anelastic piece for pressing toward the partition portion;

FIG. 13 is a front view of a spacer, which shows another shape of theelastic piece provided on the spacer in FIG. 12;

FIG. 14 is a front view of a spacer, which shows yet another shape ofthe elastic piece provided on the spacer in FIG. 12;

FIG. 15 is a cross-sectional view showing one example in which the oilsump is funnel shaped;

FIG. 16 is a cross-sectional view showing a fourth exemplary embodimentof the invention;

FIG. 17 is a cross-sectional view showing a fifth exemplary embodimentof the invention;

FIG. 18 is a cross-sectional view showing a sixth exemplary embodimentof the invention;

FIG. 19 is a cross-sectional view showing a seventh exemplary embodimentof the invention;

FIG. 20 is a cross-sectional view showing an eighth exemplary embodimentof the invention;

FIG. 21 is a cross-sectional view showing a ninth exemplary embodimentof the invention;

FIG. 22 is a cross-sectional view showing a tenth exemplary embodimentof the invention;

FIG. 23 is a cross-sectional view showing an eleventh exemplaryembodiment of the invention;

FIG. 24 is a cross-sectional view showing the eleventh exemplaryembodiment of the invention;

FIG. 25 is a cross-sectional view showing a twelfth exemplary embodimentof the invention;

FIG. 26 is a cross-sectional view showing a thirteenth exemplaryembodiment of the invention;

FIG. 27 is a cross-sectional view showing the thirteenth exemplaryembodiment of the invention;

FIG. 28 is a cross-sectional view showing a fourteenth exemplaryembodiment of the invention;

FIG. 29 is a cross-sectional view showing the fourteenth exemplaryembodiment of the invention;

FIG. 30 is a cross-sectional view showing a fifteenth exemplaryembodiment of the invention;

FIG. 31 is a cross-sectional view showing the fifteenth exemplaryembodiment of the invention;

FIG. 32 is a cross-sectional view showing a sixteenth exemplaryembodiment of the invention;

FIG. 33 is a representative view illustrating the state of loads actingin a planetary gearset of a related art; and

FIG. 34 is another representative view illustrating the state of theloads acting on the planetary gearset of the related art.

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS First Embodiment

Next, a first exemplary embodiment of this invention shall be describedwith reference to a specific example shown in the drawings. In brief,one example of a planetary gearset 11 that is the object of thisinvention is a so-called single pinion type planetary gearset of a wellknown configuration, as shown in FIG. 3, which includes as its maincomponents a sun gear 12, a ring gear 13 disposed on the same axis asthe sun gear 12, and a carrier 15 that rotatably retains a plurality ofpinion gears 14 (planet gears) meshed with the sun gear 12 and the ringgear 13. The ring gear 13 is rotatably supported via a bearing 17 by apredetermined fixed portion, e.g., a casing 16.

Also, external teeth 18 are formed on the outer peripheral surface ofthe ring gear 13. Further, a counter gear 19 which corresponds to anexternal member of this invention is disposed at a predeterminedposition on the outer peripheral side of the ring gear 13, i.e., at apredetermined position that is eccentric with respect to the planetarygearset 11. Further, this counter gear 19 and the external teeth 18 onthe ring gear 13 are meshed. Accordingly, the portion at which the teethof these two gears mesh is the location at which torque is transmitted(hereinafter, referred to as “torque transmitting point”) P. There isalmost no change in this point in the circumferential direction.

The planetary gearset 11 shown in FIG. 3 has the carrier 15 as a fixedelement that is coupled in a non-rotating state to the casing 16 viapredetermined coupling means 20. This coupling means 20 is of aparticular structure that allows the carrier 15 to move in apredetermined radial direction without rotating. That radial directionis a direction in which a load generated by torque transmitted betweenthe counter gear 19 and the ring gear 13 acts. Schematically speaking,that radial direction is the direction orthogonal to a line thatconnects the rotational axis of the ring gear 13 and the rotational axisof the counter gear 19. More accurately, the radial direction is thedirection after correcting that orthogonal direction with a pressureangle of the teeth face of the meshing counter gear 19 and the externalteeth 18 and a pressure angle of the teeth face of the meshing ring gear13 and the pinion gears 14.

The device used as this coupling means 20 of this kind of particularconfiguration can vary when necessary. For example a grooved spline thatallows movement in the aforementioned direction, or a ring-shapedsupport member or the like that houses an elastic member such as aspring or rubber may be used as this coupling means (also referred to as“spline”) 20.

In the planetary gearset 11, because the carrier 15 is a fixed element,one of the sun gear 12 and the ring gear 13 becomes an input element andthe other becomes an output element. Regardless of which is which,torque is transmitted between the ring gear 13 and the counter gear 19.A typical representation of this state is shown in FIGS. 1 and 2.

In the example shown, two pinion gears 14 are disposed symmetricallyopposite each other across the sun gear 12. Further, spline teeth areprovided on only a portion of the spline 20 that prevents the carrier 15from rotating, so as to allow the carrier 15 to move in theaforementioned direction. It should be noted that FIGS. 1 and 2 areshown simplified, as are FIGS. 33 and 34.

Referring to FIG. 1, when the ring gear 13 rotates to the left relativeto the counter gear 19, for example, such that the external teeth 18thereof engage with the counter gear 19, a load F from the torquetransmitted between the gears is generated in the direction to the rightin FIG. 1. In order to allow the ring gear 13 to rotate, there is apermanent gap (for example, of approximately several tens to severalhundred μ) between the ring gear 13 and the bearing 17 that supports thering gear 13. As a result, the ring gear 13 is able to move within thatrange.

Moreover, although rotation of the carrier 15, which is coupled to thering gear 13 via the pinion gears 14, is prevented by the so-calledgrooved spline 20, as described above, the carrier 15 is able to move tothe left and right in FIGS. 1 and 2. Accordingly, when the load F fromthe torque transmitted between the ring gear 13 and the counter gear 19is applied, the carrier 15 moves to the right in FIGS. 1 and 2, alongwith the ring gear 13.

FIGS. 1 and 2 show the resultant state of the planetary gearset afterthis movement. In this state, the gap between the ring gear 13 and thebearing 17 which supports the ring gear 13 is closed and the ring gear13 is prevented from moving by the casing 16. That is, the load actingto move the carrier 15 and the ring gear 13 is received by the casing16. As a result, a reaction force F′ of the same size as the load F actson the ring gear 13 from the casing 16, i.e., in the direction oppositethat of the load F.

Therefore, the load generated by the load F from the torque transmittedbetween the ring gear 13 and the external counter gear 19 does not acton the pinion gears 14. That is, only loads f1 and f2 from the torquetransmitted between the sun gear 12 and the ring gear 13 act on thepinion gears 14, and moreover, those loads f1 and f2 are equal (=FR/2).Therefore, although a radial load that is two times each of those loadsacts on the bearing of the pinion gears 14, that radial load is thenormal load from torque transmission.

As described above, in the planetary gearset 11 according to thisinvention, the load acting on the pinion gears 14 is limited to the loadfrom the transmission of torque between the sun gear 12 and the ringgear 13. The load from the transmission of torque between the ring gear13 and the external counter gear 19 does not act on the pinion gears 14,and the loads on the pinion gears 14 or the bearings thereof are equal.In other words, because cases such as that in which the load acting on aspecific pinion gear 14 becomes particularly large do not occur,characteristics such as strength and durability of a specific piniongear 14 does not restrict the characteristics, such as strength anddurability, of the entire planetary gearset 11.

According to the planetary gearset 11 described above, the carrier 15,which is a fixed element, is able to be fixed to the casing 16, which isa fixed portion, via the coupling means 20 that houses an elasticmember. With this configuration, it is possible to equalize the loadacting on the pinion gears 14 by moving the carrier 15 as describedabove. At the same time, vibration of the pinion gears 14 is able to beabsorbed by the elastic member, such that vibration and noise of theentire planetary gearset 11 are able to be eliminated or minimized.

In the specific example described above, the load from the torquetransmitted between the ring gear 13 and the external counter gear 19 isreceived by a fixed portion such as the casing 16. As a result, the loadacting on the pinion gears 14 is reduced such that the strength anddurability of a specific one of the pinion gears 14 does not restrictthe strength and durability of the entire planetary gearset 11.Alternatively, however, the load on a specific one of the pinion gears14 can also be reduced by distributing the load from the torque that istransmitted between the ring gear 13 and the external counter gear 19.An example of this is as follows.

Second Embodiment

A second exemplary embodiment of the invention will hereinafter bedescribed with reference to the drawings. FIG. 4 shows an example of theplanetary gearset 11 in which five pinion gears 14 are arranged in thecircumferential direction at equidistant intervals. The carrier 15 thatretains these pinion gears 14 is fixed to the casing 16 so as not beable to rotate or move in the radial direction. Also, the ring gear 13is meshed with the counter gear 19 by external teeth 18, just as in theforegoing example.

Accordingly, in the example shown in FIG. 4 as well, the positions ofthe pinion gears 14 are fixed, so that the location at which torque istransmitted (i.e., the torque transmitting point) between the ring gear13 and the counter gear 19, i.e., the relative positions of each of thepinion gears 14 and the engaging point of the external teeth 18 of thering gear 13 and the counter gear 19, is fixed. More specifically, twoof the pinion gears 14 are disposed separated at equal angles on bothsides of the torque transmitting point in the circumferential direction.

The other three pinion gears 14 are disposed at equidistant intervals inthe circumferential direction from those two pinion gears 14.Accordingly, the pinion gear 14 at the bottom in the FIG. 4 is disposedon the side opposite (i.e., is disposed in a location symmetricallyopposite, with respect to the center of the sun gear 12) the torquetransmitting point P in the circumferential direction. In other words,two pairs of pinion gears 14 are disposed in positions so that they aresymmetrical to each other on the left and right sides of the sun gear 12when it is divided by an imaginary line extending from the torquetransmitting point P through the center of the sun gear 12.

Because the carrier 15 which retains these pinion gears 14 is fixed, theload from the torque transmitted between the ring gear 13 and thecounter gear 19 acts on the pinion gears 14. However, none of the piniongears 14 are disposed directly below the torque transmitting point P inFIG. 4, i.e., between the torque transmitting point P and the sun gear12 on the imaginary line extending from the torque transmitting point Pthrough the center of the sun gear 12. Rather, one of the pinion gears14 is disposed in a location off of that imaginary line. As a result,the load F acts on the pinion gears 14 after being distributed inaccordance with the angle of separation from the torque transmittingpoint P. In the example in FIG. 4, the pinion gears 14 are disposed inpositions of left-right symmetry such that the load acts equally on boththe left and right sides of the carrier 15.

That is, in the example shown in FIG. 4, the load on the upper twopinion gears 14 is large, the load on the lower two pinion gears 14 issmall, and the load on the one bottom pinion gears 14 is even smaller.FIG. 5A shows one example of load distribution ratios of the piniongears 14 with the configuration shown in FIG. 4. For comparison, FIG. 5Bshows the load distribution ratios when one of the pinion gears 14 isdisposed directly below the torque transmitting point P.

As is evident by comparing FIGS. 5A and 5B, the load distribution ratiosare reduced by offsetting the pinion gears 14 in the circumferentialdirection from the point at which torque is transmitted to the externalmember. As a result, a large load is not concentrated on a specificpinion gear 14, thereby enabling the characteristics such as thestrength and durability of the entire planetary gearset 11 to beimproved.

FIG. 5C shows an example in which four pinion gears 14 are provided.Examples of the load distribution ratios of the pinion gears 14 are alsoindicated in the figure. In this case, the pinion gears 14 are inpositions of left-right symmetry across an imaginary line straight downfrom the torque transmitting point P. As a result, the largest torque onthe pinion gears 14 is able to be reduced the most.

Further, in each of the examples described above, the plurality ofpinion gears 14 are disposed at equidistant intervals. When theintervals between the pinion gears 14 can be set arbitrarily, however,it is preferable to arrange the pinion gears 14 as shown in FIG. 5D.That is, it is preferable to have a high concentration of the piniongears 14 in the area near the torque transmitting point P, and a lowconcentration of the pinion gears 14 in the area away from the torquetransmitting point P. More specifically, all of the pinion gears 14 arearranged in the area on the upper half of the carrier 15 in the exampleshown in FIG. 5D.

As shown in FIG. 5D, with this type of configuration, because the loadfrom the torque transmitted to the external member by all four piniongears 14 is distributed, the largest value of that load distributionratio becomes smaller. As a result, disadvantageous conditions withrespect to strength and durability and the like are able to be improved,thereby eliminating or minimizing a reduction in strength and durabilityof the entire planetary gearset 11.

It should be noted that the invention is not limited to the specificexamples described above. The invention may also be applied to a type ofplanetary gearset other than a single pinion type planetary gearset,such as a double pinion type or a Ravigneaux type planetary gearset.Also, the fixed element in this invention may be the sun gear or thering gear, instead of the carrier. In this case as well, similaroperation and effects to those with the foregoing specific examples canbe obtained. Further, the external member in this invention is notlimited to being a gear provided on the outer peripheral side of thering gear. That is, the external member may be a member which transmitstorque at a part in the circumferential direction to a rotating elementsuch as the ring gear, and which is arranged so that its axis iseccentric from the axis of the planetary gearset.

Third Embodiment

Next, a third exemplary embodiment of this invention shall be describedwith reference to a specific example shown in the drawings. Structuresin the third exemplary embodiment which are the same as those in thefirst and second exemplary embodiments shall be denoted by the samereference numerals used in the first and second exemplary embodiments,and descriptions thereof will be omitted. FIGS. 6 and 7 show theplanetary gearset 11 to which this third exemplary embodiment has beenapplied. This planetary gearset 11 is a so-called single pinion typeplanetary gearset just as in the first exemplary embodiment, in whichthe sun gear 12, which is a gear with external teeth, and the ring gear13, which is a gear with internal teeth, are arranged on the same axisand pinion gears 14 are arranged between the sun gear 12 and the ringgear 13. In the example shown in the figure, there are five pinion gears14, with each pinion gear 14 being meshed with both the sun gear 12 andthe ring gear 13.

The pinion gears 14 are disposed at equidistant intervals in thecircumferential direction and are retained by the carrier 15 so as to beable to rotate freely with the intervals between the pinion gears 14maintained. That is, the carrier 15 is a member in which a pair ofcircular discs arranged so as to sandwich the pinion gears 14 are linkedin a position so as not to interfere with the pinion gears 14. Fivepinion pins 26 supported at both end portions by the pair of circulardiscs that are included in the carrier 15, are arranged at equidistantintervals in the circumferential direction of the carrier 15. The piniongears 14 are then rotatably retained via pinion bearings 27 on thepinion pins 26.

A oil hole 28 is formed in each pinion pin 26, which extends from oneend face (the end face on the left side of the pinion pin 26 in FIG. 6)in the axial direction to a middle portion in the axial direction, whereit opens to the outer peripheral surface. The end portions of the pinionpins 26 go through the discs that are included in the carrier 15, suchthat the oil holes 28 open to the shaft end side.

The planetary gearset 11 is housed within a casing 29, and is retainedby a partition portion 30 formed integrally with the inner portion ofthe casing 29. That is, the partition portion 30 is a disc-shapedportion formed so as to stick out from the inside face of the casing 29in the radial direction toward the center of the casing 29. A sun gearshaft 32, which is rotatably retained via a bearing 31 fitted to theinner peripheral end portion of the partition portion 30, isspline-fitted to the inner peripheral portion of the sun gear 12.Moreover, a cylindrical portion which protrudes in the axial directionis formed at a mid portion of the partition portion 30. The ring gear 13is rotatably retained by a bearing 33 fitted to the inner peripheralside of that cylindrical portion.

The partition portion 30 is positioned on the shaft end side to whichthe oil holes 28 formed in the pinion pins 26 open. The carrier 15 fixedso as not to rotate, such that a portion thereof contacts the partitionportion 30.

An oil path 34 is formed on a side face, on the planetary gearset 11side, of the partition portion 30. This oil path 34 may have a tube-likeshape. In the example shown in the figure, however, the oil path 34 isconfigured as a groove formed in the side face of the partition portion30. Furthermore, this oil path 34 is circular and is, on the whole,centered around the center portion of the partition portion 30. Thewidths of the upper openings (i.e., the openings in the portion on theupper side when in actual use) of the oil path 34 in the figure arerelatively wide and the widths of the lower openings (i.e., the openingsbelow the mid portion) of the oil path 34 are relatively narrow. The oilpath 34 is also shaped appropriately.

Accordingly, the oil path 34 connects the end portions where the oilholes 28 of the pinion pins 26 open from the upper pinion pins 26 to thelower pinion pins 26 in that order. The upper end portion of the oilpath 34 opens to the upper side of the partition portion 30 and thelower end portion of the oil path 34 opens to the inner peripheral sideof the partition portion 30.

The oil sump 35 is also provided in a shape that changes the shape ofpart of the oil path 34. This oil path 34 is formed by changing theshape of a portion of the side wall that defines the oil path 34, atlocations corresponding to the end portions of each pinion pins 26. Theoil path 34 is intercommunicated with the pinion bearings 27, which arefitted to the pinion pins 26, via the oil holes 28 and notches (notshown) provided in the discs included in the carrier 15, and the like.

More specifically, the oil path 34 corresponding to the highest pinionpin 26 is formed as a V-shaped recessed portion. Also, the oil sump 35corresponding to the left and right pinion pins 26 located in the middleportion in the vertical direction are formed as arc-shaped recessedportions that curve upward. the oil holes 28 formed in the pinion pins26 open to the portions at the bottom of those recessed portions.Further, the oil sumps 35 corresponding to the pinion pins 26 in thevery lowest positions are curved upward in a V-shape, and the oil holes28 formed in the pinion pins 26 opens to those curved portions. In FIG.7, the location of the opening of the oil holes 28 is denoted by a “•”.Accordingly, the open end of each of the oil holes 28 is connected tothe oil path 34 in order from top to bottom.

In this way, the shape of the oil sump 35 varies. In particular, withthe example shown in the figure, the shape varies depending on theposition of the oil sump 35 in the vertical direction. That is,lubricating oil that runs down from the upper portion of the oil path 34runs directly into the highest oil sump which makes it easy for thelubricating oil to enter the oil hole 28 formed in the pinion pin 26 inthe location that corresponds to this oil sump 35. Accordingly, this oilsump 35 is formed relatively shallow. On the other hand, the lubricatingoil does not easily enter the oil holes 28 in the pinion pins 26 thatare located at the middle portion in the vertical direction, so thecorresponding oil sumps 35 are formed relatively deep. Also, the oilsumps 35 at the lowest portion are portions in the oil path 34 where thelubricating oil passing therethrough naturally collects and lubricatingoil from the inner peripheral side of the partition portion 30. Also,because the lubricating oil also flows into these low oil sumps 35 fromthe inner peripheral side of the partition portion 30, the oil path 34at these locations is formed in a simple curve.

Meanwhile, a reservoir portion 36, which is a hollow portion, is formedat the upper portion of the casing 29. This reservoir portion 36 is aportion that temporarily collects lubricating oil kicked up by therotation of proper rotating members such as gears, as well aslubricating oil sent through an oil path, not shown. The upper endportion of the oil path 34 is intercommunicated with this reservoirportion 36. That is, lubricating oil sent to the reservoir portion 36naturally runs down into the oil path 34.

Next, operation of the foregoing lubrication system shall be explained.When the system including the planetary gearset 11 is operated andlubricating oil is sent, or a predetermined rotating member is rotated,the lubricating oil runs into the reservoir portion 36 formed in theupper portion of the casing 29, where it is temporarily collected.Because the oil path 34 is intercommunicated with, and is located below,the reservoir portion 36, the lubricating oil in the reservoir portion36 naturally runs down into and along the oil path 34.

Referring to FIG. 7, the oil path 34 is shaped so that it branches offto the left and right from the highest oil sump 35. As a result,lubricating oil first runs into the highest oil sump 35, where apredetermined amount of the lubricating oil is collected. Thelubricating oil collected in the oil sump 35 is then supplied from thereto the highest pinion bearing 27 so as to lubricate it. In the exampleshown in the figure, when the lubrication oil is supplied to the pinionbearings 27 via the oil holes 28 formed in the pinion pins 26, i.e.,when the lubricating oil starts to be supplied to the oil path 34, thelubricating oil is immediately supplied to those pinion bearings 27 soas to lubricate them, so that no lack of lubrication, even temporary,will occur even at the highest pinion bearing 27.

Excess lubricating oil that exceeds the capacity of the highest oil sump35 runs down the oil path 34. Therefore, some of that excess lubricatingoil runs into the oil sumps 35 formed in the middle portion in thevertical direction, where it collects. Accordingly, the lubricating oilcaptured in these oil sumps 35 is supplied from here to the pinionbearings 27 positioned in the middle portion in the vertical directionso as to lubricate them. That is, the lubricating oil runs from the oilsumps 35 into the oil holes 28 in the oil sumps 35, and is supplied viathose oil holes 28 to the pinion bearings 27 in the middle portion inthe vertical direction so as to lubricate them. A sufficient amount ofthe lubricating oil needed for the middle pinion bearings 27 is ensuredby appropriately setting the capacity determined by the depth and thelike of those oil sumps 35.

The lubricating oil that overflowed the middle oil sumps 35 and thelubricating oil that was not captured in those oil sumps 35 is led tothe oil path 34, where it continues to run down and collect in thebottom oil sumps 35 of the oil path 34. Lubricating oil that runs infrom the inner peripheral end portion side of the partition portion 30is also collected in the bottom oil sumps 35. The lubricating oil isthen supplied to the pinion bearings 27 at the bottom portion from theoil sumps 35 through the oil holes 28 so as to lubricate the pinionbearings 27. As a result, lubricating oil is supplied as soon as thesystem that includes the planetary gearset 11 is operated, so there isno lack of lubrication even at the bottom pinion bearings 27.

The example shown in FIGS. 6 and 7 is of a planetary gearset 11 havingone pinion pin 26 disposed at the top, which corresponds to one point ofan equilateral pentagon, and the other pinion pins 26 disposed atpositions corresponding to the other four points. Alternatively,however, the pinion pins 26 may be positioned at arbitrary angles, sothe oil sump 35 of this invention may be provided at correspondinglocations. For example, FIG. 8 shows an example of the planetary gearset11 in which one pinion pin 26 is positioned near the bottom, as one ofthe points of the equilateral pentagon, and the other pinion pins 26 arepositioned corresponding to the other four points. In the example shownin this figure, the lubricating oil easily enters the oil holes 28 inthe two upper pinion pins 26, so the oil sumps 35 corresponding to thesepinion pins 26 are formed relatively shallow. On the other hand, becausethe lubricating oil does not easily enter the oil holes 28 in the pinionpins 26 in the middle portion in the vertical direction, the oil sumps35 corresponding to these pinion pins 26 are formed relatively deep sothat a large amount of lubricating oil collects there.

Also, according to the foregoing specific example, the oil sumps 35positioned in the middle portion in the vertical direction are formedbranching off from the oil path 34. However, the shape of the oil sumps35 according to this invention is not limited to that. That is, thedepth (the dimensions in the left-right direction in FIG. 6) of thegroove formed as the oil path, for example, may be made greater at thelocation corresponding to the pinion pins 26 so that the oil sump 35according to the invention forms a so-called shelf portion. Above thisshelf portion flow resistance against the lubricating oil running downis low, while below this shelf portion the flow resistance is high. As aresult, the lubricating oil tends to collect at the shelf portion.Therefore, this shelf portion may also be used as an oil sump.

Although the carrier 15 and the partition portion 30, which forms theoil path 34, contact each other, they are not integrally formed.Therefore, the it is possible that the lubricating oil led to the oilsump 35 may leak from between the carrier 15 and the partition portion30. To prevent this, it is preferable that a spacer 37 be disposedbetween the carrier 15 and the partition portion 30.

FIG. 9 shows one example of this spacer 37, and FIG. 10 shows oneexample of the spacer 37 attached. That is, the spacer 37 shown here isa substantially circular disc-shaped member that is tightly attached tothe side face of the partition portion 30 in which the oil path 34 isformed, which covers the oil path 34. Cylindrical protruding portions 38that insert into the oil holes 28 are formed in locations correspondingto the oil holes 28 in the pinion pins 26. Further, a clamp piece 39which engages with the outer peripheral surface of one of the circulardisc members included in the carrier 15 is integrally provided with thespacer 37. This clamp piece 39 is, for example, a disc spring-shapedportion in which a portion of the spacer 37 has been bent up, whichengages with the carrier 15 by the elastic force thereof. In this state,the protruding portions 38 are inserted into the oil holes 28. Further,the upper portion of the spacer 37 curves away from the side face of thepartition portion 30 so as to actively lead the lubricating oil betweenthe spacer 37 and the partition portion 30.

Accordingly when the spacer 37 is used, it is sandwiched between thecarrier 15 and the partition portion 30, thereby substantially closingoff the portion below the oil sump 35. As a result, leaking of thelubricating oil from the oil sump 35 is eliminated or minimized.Furthermore, because the protruding portion 38 actively leads thelubricating oil to the oil holes 28, it is possible to supply the pinionbearings 27 with a sufficient amount of lubricating oil.

The spacer 37 is used to close off the open end of the oil path 34 atthe side face of the partition portion 30, so it is preferable that thespacer 37 be attached to the partition portion 30 rather than to thecarrier 15. FIG. 11 shows an example of this. In the example shown here,a clamp piece 40 that protrudes on the side opposite the protrudingportion 38 is formed on the inner peripheral end portion of the spacer37. The spacer 37 attaches to the partition portion 30 by the clamppiece 40 engaging with the edge portion of the inner peripheral surfaceof the partition portion 30.

Therefore, according to the configuration shown in FIG. 11, the spacer37 reliably attaches tightly to the side face of the partition portion30 such that the leakage of the lubricating oil from the oil sump 35 canbe eliminated or minimized.

Furthermore, the spacer 37 is provided with a plurality of theprotruding portions 38 which fit into the oil holes 28 so as to positionthe spacer 37 with respect to, as well as attach it to, the carrier 15.Accordingly, the operation of positioning the spacer 37 with respect tothe carrier 15 by the protruding portions 38 and tightly attaching thespacer 37 to the partition portion 30 may be done by an elastic memberinterposed between the carrier 15 and the partition portion 30. Forexample, as shown in FIG. 12, elastic pieces 41 that protrude in thesame direction as do the protruding portions 38, i.e., toward thecarrier 15 side, may be formed in a plurality of locations on the innerperipheral edge of the spacer 37, such that these elastic pieces 41 pushon the side face of the carrier 15, and the reaction force therefrompushes the spacer 37 against the partition portion 30.

These elastic pieces 41 can be made an appropriate shape as necessary.For example, the elastic pieces 41 may have a variety of shapes such asan arc-shaped cantilever that extends in the circumferential direction,as shown in FIG. 13. Alternatively, the elastic pieces 41 may beT-shaped, with the left and right free end portions protruding in thesame direction as the protruding portion 38 and able to bend flexibly,as shown in FIG. 14.

Moreover, the oil paths and oil sumps according to this invention arenot limited to the specific examples. For example, the oil sump 35 mayalso be formed having a kind of funnel-shaped cross-section, with thelower end portion, which is cylindrical in shape, going into the oilhole 28.

The invention is not limited to the lubrication system for the foregoingsingle pinion type planetary gearset, but can be applied to alubrication system for a double pinion type planetary gearset or anothertype of planetary gearset such as a Ravigneaux type planetary gearset.

According to the foregoing exemplary embodiment of the invention, evenin a pinion bearing arranged to be relatively high by fixing thecarrier, lubricating oil is able to collect in the oil sump that isprovided in a relatively high location corresponding to that pinionbearing, and lubricating oil is supplied from there. As a result,lubricating oil is supplied to the pinion bearing located relativelyhigh quickly after lubricating oil starts to be supplied to the oilpath, such that that bearing is able to be sufficiently lubricated asrequired. Also, the speed with which the lubricating oil collects andthe amount collected differ depending on the shape of each of the oilsumps. As a result, lubricating oil at a speed and of an amountaccording to the particular shape of the oil sump can be supplied toeach pinion bearing through the oil hole in the pinion pin arrangedcorresponding to each oil sump. As a result, even if the carrier isfixed, it is possible to lubricate the pinion bearings sufficiently andwithout delay.

Next, a lubrication system 101 of the planetary gearset shown in thefirst through the third exemplary embodiments will be described. Inparticular, an exemplary embodiment of the lubrication system 101 thatsupplies lubricating oil to the reservoir and then supplies thelubricating oil to portions requiring lubrication such as the pinionbearings 27 of the planetary gearset, as shown in the third exemplaryembodiment, will be described with reference to the drawings.

Fourth Embodiment

The lubrication system 101 shown in FIG. 16 has a container (i.e., atray) 102. This container (tray) 102 has a first retaining portion 103,a second retaining portion 104, and an oil reservoir 105. First, thefirst retaining portion 103 has a cross section in the height directionthat is substantially arc-shaped. The first retaining portion 103 isformed over an area of approximately 270 degrees, with an opening 106formed between both ends of the first retaining portion 103 in thecircumferential direction. A lubricating oil sump A1 is formed in aninner portion 103A of the first retaining portion 103, where a firstgear 107 is also arranged. A portion of this first gear 107 is submersedin the lubricating oil sump A1. The first gear 107 rotatescounterclockwise around a rotation axis B1.

The second retaining portion 104 has a cross section in the heightdirection that is substantially arc-shaped. The second retaining portion104 is formed over an area of approximately 120 degrees. A connectingportion 110 is formed where one end of the second retaining portion 104in the circumferential direction is connected with one end of the firstretaining portion 103. A lubricating oil sump C1 is formed on therecessed side (i.e., the upper surface side) of the second retainingportion 104, where a second gear 108 is also arranged. The second gear108 is attached to a second rotating shaft (not shown), which rotatesclockwise around a rotation axis D1. A lower edge portion 109 on theouter periphery of the second gear 108 is disposed lower than the upperedge of the connecting portion 110. Accordingly, a portion of the outerperiphery of the second gear 108 is submersed in the lubricating oilsump C1. It should be noted that the first gear 107 and the second gear108 are not engaged. Moreover, the first rotating shaft and the secondrotating shaft are both horizontal and both rotate around a parallelaxis (not shown). Power is transmitted between the first rotating shaftand the second rotating shaft by a transmitting member (not shown).

The oil reservoir 105 has a cross-sectional shape in the heightdirection of an upside-down trapezoid with a bottom side, a right side,and a left side. A connecting portion 111 is formed where one end of theoil reservoir 105 and one end of the second retaining portion 104 areconnected. The height of an upper edge portion 112 of the first gear 107is set to a height between the rotation axis D1 and the upper edge ofthe connecting portion 110. Further, the first gear 107 and the secondgear 108 are arranged in substantially the same location in the axialdirection on the first rotating shaft and the second rotating shaft,respectively. Also, the height of the rotation axis D1 and the height ofthe upper edge of the connecting portion 111 are set to be substantiallythe same. Moreover, the opening 106 is arranged between the rotationaxis B1 and the rotation axis D1. That is, the opening 106 is arrangedbetween the first gear 107 and the second gear 108.

In the lubrication system 101 of the above configuration, the first gear107 and the second gear 108 rotate following the transmission of powerbetween at least one of an engine and an electric motor, and wheels. Thelubricating oil collected in the lubricating oil sump A1 is sent in thecircumferential direction while adhering to the first gear 107 andthrown toward the outside of the first gear 107 by centrifugal force asthe first gear 107 rotates counterclockwise.

Some of the lubricating oil thrown off in this way is thrown through theopening 106 and toward the top face of the second retaining portion 104.Once above the second retaining portion 104, the lubricating oil thennaturally runs down and forms the lubricating oil sump C1. When thishappens, the lubricating oil in the lubricating oil sump C1 is thenkicked up by the second gear 108 and thrown upward by centrifugal force,after which it then naturally comes down and is collected in an innerportion 105A of the oil reservoir 105. The lubricating oil sent to theinner portion 105A of the oil reservoir 105 is then sent to portionsrequiring lubrication, such as an electric motor, a generator, engagingportions of gears, and bearings, via an oil path (not shown). Theportions requiring lubrication are then lubricated and cooled by thelubricating oil. Accordingly, overheating and wear and the like ofportions requiring lubrication is suppressed, thus improving thedurability and extending the life of those portions.

In this way, according to the exemplary embodiment shown in FIG. 16, thelubricating oil from the lubricating oil sump A1 is supplied to theportions requiring lubrication in a plurality of steps, the first beingthe transfer of the lubricating oil by rotation of the first gear 107,and the second being the transfer of the lubricating oil by rotation ofthe second gear 108. Accordingly, even if the first retaining portion103 is separated from the oil reservoir 105, a reduction in the amountof lubricating oil supplied to the oil reservoir 105 is able to besuppressed. Therefore, the layout with respect to relative positions ofthe oil reservoir 105 and the first gear 107 in the height direction isnot restricted, thereby increasing the degree of freedom.

Also, because the lubricating oil transferred by the first gear 107 isreceived by the second gear 108 and then supplied to the oil reservoir105, the lubricating oil can be supplied to the oil reservoir 105 whenthe oil reservoir 105 is separated from the first gear 107, regardlessof the rotation speed of the first gear 107. In other words, the amountof lubricating oil supplied to the oil reservoir 105 can be ensuredwithout increasing the surface area of the first gear 107 that issubmersed in the lubricating oil sump A1. As a result, an increase inpower loss between the rotating shafts is able to be suppressed.

Still further, the lubricating oil can be supplied to the oil reservoir105 from above the upper edge of the connecting portion 111 that ishigher than the upper edge 112 of the first gear 107. Moreover, becausethe lubricating oil is retained by the teeth grooves formed between theteeth of the second gear 108, it is possible to improve the lubricatingoil retaining function of the second gear 108.

Here, with respect to the corresponding relationship between thestructures of the exemplary embodiment shown in FIG. 16 and thestructures of this invention, the first gear 107 corresponds to thefirst rotating body of this invention, the oil reservoir 105, electricmotor, generator, engaging portions between gears, bearings, and thelike correspond to portions requiring lubrication of this invention, thesecond gear 108 corresponds to the second rotating body of thisinvention, the lubricating oil sump C1 corresponds to the middlelubricating oil sump of this invention, the teeth grooves between eachof the teeth formed on the outer periphery of the second gear 108correspond to recessed portions of the invention, the upper edge of theconnecting portion 111 corresponds to the upper edge of one of theportions requiring lubrication of the invention, the first rotatingshaft and the second rotating shaft and the like correspond to rotatingmembers for transmitting power, and the lubricating oil sump A1corresponds to the main lubricating oil sump of the invention.

Fifth Embodiment

Structures of the lubrication system 101 shown in FIG. 17 which are thesame as those in the lubrication system 101 shown in FIG. 16 shall bedenoted by the same reference numerals used in FIG. 16, and descriptionsthereof will be omitted. In FIG. 17 the second retaining portion 104 isformed in an arc shape over an area of 300 degrees or more. The secondretaining portion 104 has a first arc-shaped portion 117 near theopening 106. A passage 113 is formed in a location in the secondretaining portion 104 closest to the opening 106, i.e., in the firstarc-shaped portion 117. This passage 113 passes through the secondretaining portion 104 in the direction of thickness. The passage 113 andthe upper edge 112 of the first gear 107 are arranged to be atsubstantially the same height.

Also, an opening 115 is formed in the second retaining portion 104 in alocation corresponding to an upper edge 114 of the second gear 108. Theopening 115 is formed between the first arc-shaped portion 117 and thesecond arc-shaped portion 118. In the exemplary embodiment shown in FIG.17, the second arc-shaped portion 118 serves as both a portion of thesecond retaining portion 104 in the circumferential direction, as wellas a portion of the oil reservoir 105. An upper edge 116 of the secondarc-shaped portion 118 is positioned higher than the upper edge 114 ofthe second gear 108.

According to the exemplary embodiment shown in FIG. 17, when the firstrotating shaft and the second rotating shaft are rotated, the first gear107 and the second gear 108 both rotate counterclockwise. Here, therotation speed of the second gear 108 is faster than that of the firstgear 107. The lubricating oil kicked up by the rotation of the firstgear 107 is thrown through the opening 106 toward the outer face of thesecond retaining portion 104. Some of this lubricating oil that isthrown toward the outer face of the second retaining portion 104 passesthrough the passage 113 and runs into an inner portion 104A of thesecond retaining portion 104.

In this way, the lubricating oil sump C1 forms in the inner portion 104Aof the second retaining portion 104. The lubricating oil in thelubricating oil sump C1 is kicked up by the rotation of the second gear108 and thrown by centrifugal force through the opening 115 so that itpasses over the upper edge 116 and into the oil reservoir 105.Therefore, the component parts in the fifth exemplary embodiment thatare the same as those in the fourth exemplary embodiment provide thesame operation and effects obtained in the fourth exemplary embodiment.

Sixth Embodiment

The structures of the lubrication system 101 shown in FIG. 18 that arethe same as those in the exemplary embodiment shown in FIGS. 16 and 17shall be denoted by the same reference numerals as in FIGS. 16 and 17,and descriptions thereof will be omitted. The second retaining portion104 has a wall portion 119 that extends in the height direction. Thiswall portion 119 serves as both a portion of the second retainingportion 104 and a portion of the oil reservoir 105. An upper edge 120 ofthe wall portion 119 is provided that is higher than an upper edge 114of the second gear 108. A guide member 121 that extends toward the upperedge 114 of the second gear 108 is continuous from the upper edge 120 ofthe wall portion 119. The guide member 121 is plate shaped, with an topface thereof slanting downward toward the upper edge 114 of the secondgear 108. The opening 115 is formed between the free end of the guidemember 121 and the end portion of the first arc-shaped portion 117 inthe circumferential direction.

In the sixth exemplary embodiment as well, when the first gear 107 andthe second gear 108 rotate counterclockwise, the lubricating oil sump C1is formed by the same operation as in the second exemplary embodiment.The rotation speed of the second gear 108 is faster than that of thefirst gear 107, so the centrifugal force acting on the lubricating oilis also greater on the second gear 108 side than it is on the first gear107 side. The lubricating oil thrown upward by the second gear 108passes through the opening 115 and lands on the top face of the guidemember 121. This lubricating oil then rises up the top face of the guidemember 121 by the inertial force when it was thrown upward by the secondgear 108 and runs into the oil reservoir 105.

The component parts in the sixth exemplary embodiment that are the sameas those in the fourth and fifth exemplary embodiments provide the sameoperation and effects obtained in the fourth and fifth exemplaryembodiments. Furthermore, in the sixth exemplary embodiment, the guidemember 121 is disposed between the opening 115 and the space above theoil reservoir 105. As a result, the lubricating oil kicked up by thefirst gear 107 can be reliably supplied to the oil reservoir 105regardless of the distance between the first gear 107 and the oilreservoir 105 in the height direction. The corresponding relationshipbetween the structures of the sixth exemplary embodiment and thestructures of this invention is the same as the correspondingrelationship between the structures of the fourth exemplary embodimentand the structures of the invention.

Seventh Embodiment

The structures of the lubrication system 101 shown in FIG. 19 that arethe same as those in the exemplary embodiment shown in FIGS. 16 and 17shall be denoted by the same reference numerals as in FIGS. 16 and 17,and descriptions thereof will be omitted. In FIG. 19, a guide member 122is provided substantially horizontal to the side the first gear 107. Theguide member 122 is plate shaped. There is a slight gap between thisguide member 122 and a side face (or end face) 123 of the first gear107. If the material of the side face 123 is of low strength (e.g., anelastomer or the like), the guide member 122 may contact the side face123 of the first gear 107. The side face 123 of the first gear 107refers to the face orthogonal to the axis of the first rotating shaft.

This guide member 122 is provided at a height between the upper edge 112of the first gear 107 and the rotational axis B1. The end portion of theguide member 122 on the side opposite the first gear 107 is connected tothe second retaining portion 104. The top face of the guide member 122and the lower edge of the inner face of the passage 113 are set to be atsubstantially the same height. In FIG. 19, one guide member 122 isarranged on one side face 123 of the first gear 107. Alternatively,however, two of the guide members 122 may be attached separately to theside face 123 on both sides of the first gear 107.

The component parts in the exemplary embodiment shown in FIG. 19 thatare the same as those in the exemplary embodiment shown in FIGS. 16 and17 provide the same operation and effects obtained in the exemplaryembodiments shown in FIGS. 16 and 17. Moreover, in the exemplaryembodiment shown in FIG. 19, some of the lubricating oil kicked up bythe first gear 107 is picked up by the guide member 122. Morespecifically, the lubricating oil that is adhered to the side face 123of the first gear 107 is picked up by the guide member 122. Thislubricating oil then moves (runs) over the top face of the guide member122 toward the passage 113 by inertial force when it comes off of thefirst gear 107. After passing through the passage 113, the lubricatingoil runs into the inner portion 104A of the second retaining portion104, from which it is transferred to the oil reservoir 105 as describedabove.

Also, in the exemplary embodiment shown in FIG. 19, if the first gear107 rotates at high speed, the lubricating oil thrown off by centrifugalforce passes through the passage 113 and runs into the inner portion104A of the second retaining portion 104. On the other hand, if thefirst gear 107 rotates at low speed such that the lubricating oil thrownupward by centrifugal force does not reach the passage 113, thelubricating oil adhered to the first gear 107 by viscosity and shearingresistance is then picked up by the side face 123 and transferred to theoil reservoir 105. Accordingly, it is possible to ensure the amount oflubricating oil supplied to the oil reservoir 105 regardless of therotation speed of the first gear 107 (as long as the first gear 107 isnot stopped). Providing two of the guide members 122 further increasesthe amount of lubricating oil picked up from the first gear 107. Thecorresponding relationship between the structures shown in FIG. 19 andthe structures of this invention is the same as the correspondingrelationship between the structures shown in FIG. 15 and the structuresof this invention.

Eighth Embodiment

The structures of the lubrication system 101 shown in FIG. 20 that arethe same as those in the exemplary embodiment shown in FIGS. 16 and 19shall be denoted by the same reference numerals as in FIGS. 16 and 19,and descriptions thereof will be omitted. In the exemplary embodimentshown in FIG. 20, a third gear 124 that engages with the first gear 107is provided. This third gear 124 is mounted on a third rotating shaft(not shown). Further, the first gear 107 and the third gear 124 are bothhelical gears. In the exemplary embodiment shown in FIG. 20, as well,the first gear 107 and the second gear 108 rotate counterclockwise, andthe third gear 124 rotates clockwise. The component parts in theexemplary embodiment shown in FIG. 20 that are the same as those in theexemplary embodiment shown in FIGS. 16 and 19 provide the same operationand effects obtained in the exemplary embodiments shown in FIGS. 16 and19.

Also, in the exemplary embodiment shown in FIG. 20, because the firstgear 107 and the third gear 124 are both helical gears, the contactportion, or so-called contact point, between the tooth face of the teethof the first gear 107 and the tooth face of the teeth of the third gear124 moves in the tooth trace direction of the teeth as the first gear107 and the third gear 124 rotate. Therefore, the lubricating oilretained in the tooth grooves between the teeth of the first gear 107 ispushed out in the tooth trace direction of the teeth as the contactpoint between the teeth of the first gear 107 and the teeth of the thirdgear 124 moves. In other words, the lubricating oil moves from the pointwhere engagement starts toward the point where engagement ends.

In this way, the lubricating oil that has moved in the tooth tracedirection of the teeth is then pushed out onto the guide member 122.That is, in the exemplary embodiment shown in FIG. 20, the lubricatingoil adhered to the side face 123 of the first gear 107, as well as thelubricating oil retained in the teeth grooves of the first gear 107 areboth transferred to the inner portion 104A of the second retainingportion 104 via the top face of the guide member 122. Therefore, theamount of lubricating oil supplied to the oil reservoir 105 is able tobe increased as quickly as possible.

Also, by pushing the lubricating oil retained in the teeth grooves ofthe first gear 107 out in the tooth trace direction, the amount oflubricating oil transferred to the guide member 122 is able to beensured. Accordingly, even if the gap between the guide member 122 andthe side face 123 of the first gear 107 is not made very narrow, theamount of lubricating oil is still able to be ensured. As well, even ifthe rotation speed of the first gear 107 is low, it is still possible toensure the amount of lubricating oil transferred to the oil reservoir105. The guide member 122 is obviously disposed near the side face 123that is close to the point where engagement ends. With respect to thecorresponding relationship between the structures of the exemplaryembodiment shown in FIG. 20 and the structures of this invention, theteeth of the first gear 107 and the teeth of the third gear 124correspond to pushing mechanisms of the invention. The correspondingrelationship of the other structures of the exemplary embodiment shownin FIG. 20 and the structures of the invention is the same as thecorresponding relationship between the structures of the exemplaryembodiments shown in FIGS. 16 and 19 and the structures of theinvention.

Ninth Embodiment

A ninth exemplary embodiment of the invention is shown in FIG. 21. Thestructures of the lubrication system 101 shown in FIG. 21 that are thesame as those in the exemplary embodiment shown in FIGS. 16, 17, and 19shall be denoted by the same reference numerals as in FIGS. 16, 17, and19, and descriptions thereof will be omitted. In the exemplaryembodiment shown in FIG. 21, a guide member 125 continuous on from theupper edge of the second arc-shaped portion 118 of the second retainingportion 104. This guide member 125 extends to the side of the secondgear 108, and there is a predetermined gap between the guide member 125and a side face 126 of the second gear 108. Alternatively, two of theguide members 125 may be attached to the second gear 108, one guidemember 125 being attached to each side face 126 of the second gear 108.The component parts in the exemplary embodiment shown in FIG. 21 thatare the same as those in the exemplary embodiment shown in FIGS. 16, 17,and 19 provide the same operation and effects obtained in the exemplaryembodiments shown in FIGS. 16, 17, and 19.

Also, in the exemplary embodiment shown in FIG. 21, the lubricating oiladhered to the side face 126 of the second gear 108 is picked up by theguide member 125 as the second gear 108 rotates, and the lubricating oilon the top face of the guide member 125 runs toward the oil reservoir105 from the inertial force when it is picked up from the second gear108. That is, in the exemplary embodiment shown in FIG. 21, both thelubricating oil adhered to the side face 123 of the first gear 107 andthe lubricating oil adhered to the side face 126 of the second gear 108are able to be transferred to the oil reservoir 105. Accordingly, theamount of lubricating oil provide to the oil reservoir 105 can beincreased as quickly as possible. The corresponding relationship of theother structures of the exemplary embodiment shown in FIG. 21 and thestructures of the invention is the same as the correspondingrelationship between the structures of the exemplary embodiments shownin FIGS. 16, 17, and 19 and the structures of the invention.

Tenth Embodiment

A tenth exemplary embodiment of the invention is shown in FIG. 22. Thestructures of the lubrication system 101 shown in FIG. 22 that are thesame as those in the exemplary embodiment shown in FIGS. 16, 17, 19, and21 shall be denoted by the same reference numerals as in FIGS. 16, 17,19, and 21, and descriptions thereof will be omitted. In the exemplaryembodiment shown in FIG. 22, a third gear 127 that engages with thesecond gear 108 is provided. This third gear 127 is mounted on a thirdrotating shaft (not shown). The second gear 108 and the third gear 127are both helical gears. The component parts in the exemplary embodimentshown in FIG. 22 that are the same as those in the exemplary embodimentshown in FIGS. 16, 17, 19, and 21 provide the same operation and effectsobtained in the exemplary embodiments shown in FIGS. 16, 17, 19, and 21.

Also, in the exemplary embodiment shown in FIG. 22, the second gear 108rotates counterclockwise and the third gear 127 rotates clockwise. Inthe exemplary embodiment shown in FIG. 22, because both the second gear108 and the third gear 127 are helical gears, the contact portion, orso-called contact point, between the tooth face of the teeth of thesecond gear 108 and the tooth face of the teeth of the third gear 127moves in the tooth trace direction of the teeth as the second gear 108and the third gear 127 rotate. Therefore, the lubricating oil retainedin the tooth grooves between the teeth of the second gear 108 is pushedout in the tooth trace direction of the teeth as the contact pointbetween the teeth of the second gear 108 and the teeth of the third gear127 moves. In other words, the lubricating oil moves from the pointwhere engagement starts toward the point where engagement ends.

In this way, the lubricating oil that has moved in the tooth tracedirection of the teeth is then pushed out onto the guide member 125.That is, in the exemplary embodiment shown in FIG. 22, the lubricatingoil adhered to the side face 126 of the second gear 108, as well as thelubricating oil retained in the teeth grooves of the second gear 108 aretransferred to the oil reservoir 105 via the top face of the guidemember 125. Therefore, the amount of lubricating oil supplied to the oilreservoir 105 is able to be increased as quickly as possible.

Also, by pushing the lubricating oil retained in the teeth grooves ofthe second gear 108 out in the tooth trace direction, the amount oflubricating oil transferred to the guide member 125 is able to beensured. Accordingly, even if the gap between the guide member 125 andthe side face 126 of the second gear 108 is not made very narrow, theamount of lubricating oil is still able to be ensured. As well, even ifthe rotation speed of the second gear 108 is low, it is still possibleto ensure the amount of lubricating oil transferred to the oil reservoir105. The guide member 125 is obviously disposed near the side face 126that is close to the point where engagement ends. With respect to thecorresponding relationship between the structures of the exemplaryembodiment shown in FIG. 22 and the structures this invention, the teethof the second gear 108 and the teeth of the third gear 127 correspond topushing mechanisms of the invention. The corresponding relationship ofthe other structures of the exemplary embodiment shown in FIG. 22 andthe structures of the invention is the same as the correspondingrelationship between the structures of the exemplary embodiments shownin FIGS. 16, 17, 19, and 21 and the structures of the invention.

Eleventh Embodiment

An eleventh exemplary embodiment of the invention is shown in FIGS. 23and 24. The container 102 disposed inside the casing has a firstretaining portion 131. This first retaining portion 131 has asubstantially arc-shaped cross section in the height direction. Thefirst retaining portion 131 is formed over an area of approximately 180degrees, and an opening 134A is formed between one end portion 132 andanother end portion 133 in the circumferential direction. Further, theoil reservoir 105 is formed continuous with the first retaining portion131. The first retaining portion 131 also serves as a portion of the oilreservoir 105.

A guide member 134 continues from the end portion 132 which, of the endportion 132 and the 133, is on the side opposite the oil reservoir 105.This guide member 134 has a horizontal portion 135 and a verticalportion 136. The horizontal portion 135 protrudes toward the outside ofthe first retaining portion 131. A recessed portion 137 is formedextending along the inner face of the horizontal portion 135 and theinner face of the vertical portion 136. Here, “inner face” refers to theface that faces an inner portion 131A of the first retaining portion131. A portion of the horizontal portion 135 extends to the side of theside face of a first gear 129 on the side near a second gear 130.

Meanwhile, a rotating shaft 128 is provided inside a casing (not shown).The first gear 129 and the second gear 130 are mounted on this rotatingshaft 128. The first gear 129 and the second gear 130 rotatecounterclockwise in FIG. 23. The diameter of the tip circle of the teethof the first gear 129 is larger than the diameter of the tip circle ofthe teeth of the second gear 130. The first gear 129 and the second gear130 are arranged in the inner portion 131A of the first retainingportion 131. A portion of the first gear 129 is exposed to the outsidethrough the opening 134A. Furthermore, a third gear 138 which engageswith the first gear 129 is provided.

The third gear 138 is arranged above the guide member 134. The firstgear 129 and the third gear 138 are both helical gears, and the contactpoint between the first gear 129 and the third gear 138 is between anupper edge 139 of the first gear 129 and the recessed portion 137 in thecircumferential direction of the first gear 129. Also, the area in whichthe recessed portion 137 is provided is made to be the area thatincludes the first gear 129 and the second gear 130 in the axialdirection of the rotating shaft 128.

In FIGS. 23 and 24, the lubricating oil in the lubricating oil sump A1which is inside the first retaining portion 131 is kicked up by therotation of the first gear 129. In the exemplary embodiment shown inFIGS. 23 and 24, because the first gear 129 and the third gear 138 areboth helical gears, the contact portion, or so-called contact point,between the tooth face of the teeth of the first gear 129 and the toothface of the teeth of the third gear 138 moves in the tooth tracedirection of the teeth as the first gear 129 and the third gear 138rotate. Therefore, the lubricating oil retained in the tooth groovesbetween the teeth of the first gear 129 is pushed out in the tooth tracedirection of the teeth as the contact point between the teeth of thefirst gear 129 and the teeth of the third gear 138 moves. In otherwords, the lubricating oil moves from the point where engagement startstoward the point where engagement ends.

In this way, the lubricating oil that has moved in the tooth tracedirection of the teeth runs into the recessed portion 137. Thelubricating oil that has run into the recessed portion 137 then movestoward the second gear 130 side by inertial force from the movement inthe tooth trace direction, and adheres to the second gear 130. Thelubricating oil is then thrown upward by the centrifugal force from therotation of the second gear 130 and runs into the oil reservoir 105.

In the eleventh exemplary embodiment, the lubricating oil is transferredin a plurality of steps, the first being the transfer of the lubricatingoil by rotation of the first gear 129, and the second being the transferof the lubricating oil by rotation of the second gear 130. Accordingly,even if the first retaining portion 131 is separated from the oilreservoir 105, a reduction in the amount of lubricating oil supplied tothe oil reservoir 105 is able to be suppressed.

Also, because the lubricating oil is retained by the tooth grooves ofthe second gear 130, the lubricating oil retaining function of thesecond gear 130 is improved. Further, the lubricating oil is alsotemporarily retained in the recessed portion 137. Accordingly, thelubricating oil supplying function is improved even if the first gear129 and the second gear 130 are separated by a large distance. Also,because the lubricating oil retained in the first gear 129 is pushed outin the tooth trace direction by the meshing of the first gear 129 andthe second gear 130, the ability of the lubricating oil that is adheredthe first gear 129 to separate therefrom is improved. Moreover, thelubricating oil is able to be supplied to the oil reservoir 105regardless of the rotation speed of the first gear 129. Furthermore, itis possible to suppress an increase in the surface area of the firstgear 129 that is submersed in the lubricating oil.

Twelfth Embodiment

FIG. 25 is a diagram showing another configuration of the eighthexemplary embodiment. The structures of the lubrication system 101 shownin FIG. 25 that are the same as those in the exemplary embodiment shownin FIGS. 23 and 24 shall be denoted by the same reference numerals as inFIGS. 23 and 24, and descriptions thereof will be omitted. Also, in theexemplary embodiment shown in FIG. 25, the wall portion 119 that extendsin the height direction is continuous from the end portion of the firstretaining portion 131 on the side opposite the end portion 132. Theupper edge of the wall portion 119 continues to the bottom portion ofthe oil reservoir 105. A guide member 140 that extends toward the upperedge 139 of the second gear 130 continues from an upper edge 141 of theoil reservoir 105. The guide member 140 is plate-shaped, with the topface slanted downward toward the upper edge 139 of the second gear 130.The upper edge 139 is higher than the upper edge 142 of the first gear129.

The component parts in the twelfth exemplary embodiment that are thesame as those in the eleventh exemplary embodiment provide the sameoperation and effects obtained in the eleventh exemplary embodimentshown in FIG. 23. Further, in the twelfth exemplary embodiment, therotation speed of the second gear 130 is faster than that of the firstgear 129. The lubricating oil retained by the second gear 130 is thenthrown upward by centrifugal force and moves up along the top face ofthe guide member 140, after which it passes over the upper edge 141 andruns into the inner portion 105A of the oil reservoir 105. In this way,according to the twelfth exemplary embodiment, because the guide member140 is provided, the lubricating oil clears the upper edge 141 that ishigher than the upper edge 142 of the first gear 129, and is transferredto the oil reservoir 105. Accordingly, it is possible to reliably supplylubricating oil to the oil reservoir 105 when that oil reservoir 105 ishigher than the upper edge 142 of the first gear 129.

Thirteenth Embodiment

A thirteenth exemplary embodiment is shown in FIGS. 26 and 27. Thestructures shown in FIGS. 26 and 27 that are the same as those shown inFIGS. 23 and 24 shall be denoted by the same reference numerals as inFIGS. 23 and 24, and descriptions thereof will be omitted. In thethirteenth exemplary embodiment, a guide member 143 continues from aportion of the first retaining portion 131 that also serves as a portionof the oil reservoir 105. This guide member 143 is plate-shaped andextends substantially horizontal. The component parts in the thirteenthexemplary embodiment that are the same as those in the eleventhexemplary embodiment provide the same operation and effects obtained inthe eleventh exemplary embodiment. Further, lubricating oil adhered tothe side face of the second gear 130 is picked up by the guide member143 and moved along the top face of the guide member 143, whereby it issupplied to the oil reservoir 105. Accordingly, it is possible toincrease the amount of lubricating oil supplied to the oil reservoir 105as quickly as possible.

Fourteenth Embodiment

A fourteenth exemplary embodiment is shown in FIGS. 28 and 29. Thestructures shown in FIGS. 28 and 29 that are the same as those shown inFIGS. 26 and 27 shall be denoted by the same reference numerals as inFIGS. 26 and 27, and descriptions thereof will be omitted. In thefourteenth exemplary embodiment, the second gear 130 is engaged with afourth gear 144. The second gear 130 and the fourth gear 144 are bothhelical gears. The area where the second gear 130 and the fourth gear144 engage is above the top face of the guide member 143. The componentparts in the fourteenth exemplary embodiment that are the same as thosein the thirteenth exemplary embodiment provide the same operation andeffects obtained in the thirteenth exemplary embodiment.

Also, in the fourteenth exemplary embodiment, because the second gear130 and the fourth gear 144 are both helical gears, the contact pointbetween the tooth face of the teeth of the second gear 130 and the toothface of the teeth of the fourth gear 144 moves in the tooth tracedirection of the teeth as the second gear 130 and the fourth gear 144rotate. Therefore, the lubricating oil retained in the tooth groovesbetween the teeth of the second gear 130 is pushed out in the toothtrace direction of the teeth as the contact point between the teeth ofthe second gear 130 and the teeth of the fourth gear 144 moves. In otherwords, the lubricating oil moves from the point where engagement startstoward the point where engagement ends.

In this way, the lubricating oil that has moved in the tooth tracedirection of the teeth is then pushed out onto the guide member 143.That lubricating oil, as well as the lubricating oil picked up from theside face of the second gear 130, are then transferred to the oilreservoir 105. Therefore, the amount of lubricating oil supplied to theoil reservoir 105 is able to be increased as quickly as possible.

Fifteenth Embodiment

A fifteenth exemplary embodiment is shown in FIGS. 30 and 31. Acontainer 150 is arranged inside a casing (not shown), and a first gear153 and a second gear 152 are arranged in an inner portion 151 of thecontainer 150. The second gear 152 is mounted on a first rotating shaft(not shown) and the first gear 153 is mounted on a second rotating shaft157. The first rotating shaft and the second rotating shaft 157 bothrotate around a horizontal axis. The first gear 153 and the second gear152 are both helical gears and are engaged together. The second gear 152is arranged above the first gear 153.

A first arc-shaped face 154 and a second arc-shaped face 155 are formedon the inner face of the container 150. The first arc-shaped face 154 isprovided along the edge of the second gear 152, and the secondarc-shaped face 155 is provided along the edge of the first gear 153. Anopening 156 is formed above the inner portion 151 in an upper portion ofthe container 150. Also, a guide member 158 is formed on the innerportion 151 of the container 150. This guide member 158 has asubstantially U-shaped cross section in the vertical direction. That is,the guide member 158 has an upper plate 159, a side plate 160, and alower plate 161.

A recessed portion 162 is formed in the space surrounded by the upperplate 159, the side plate 160, and the lower plate 161. This recessedportion 162 is arranged substantially horizontal to a side of the areawhere the second gear 152 and the first gear 153 engage. One end portionof the recessed portion 162 in the horizontal direction is closed by awall 165. The lower plate 161 is arranged near a side face 163 of thefirst gear 153. The lubricating oil sump A1 is formed in the innerportion 151 of the container 150. Furthermore, a portion of thecontainer 150 also serves as a portion of a oil reservoir 164.

In FIG. 30, the first gear 153 rotates counterclockwise and the secondgear 152 rotates clockwise. Because a lower portion of the first gear153 is submersed in the lubricating oil sump A1, lubricating oil iskicked up by the rotation of the first gear 153. Lubricating oil adheredto the side face 163 of the first gear 153 is then picked up by thelower plate 161 and retained in the recessed portion 162.

Also, because the first gear 153 and the second gear 152 are bothhelical gears, the contact point between the tooth face of the teeth ofthe first gear 153 and the tooth face of the teeth of the second gear152 moves in the tooth trace direction of the teeth as the first gear153 and the second gear 152 rotate. Therefore, the lubricating oilretained in the tooth grooves between the teeth of the first gear 153 ispushed out in the tooth trace direction of the teeth as the contactpoint moves. In other words, the lubricating oil moves from the pointwhere engagement starts toward the point where engagement ends.

In this way, the lubricating oil that has moved in the tooth tracedirection of the teeth runs into the recessed portion 162. Because thelubricating oil that has run into the recessed portion 162 contacts thesecond gear 152, it moves toward the wall 165 as the second gear 152rotates. This lubricating oil is then retained by the tooth grooves ofthe second gear 152 and thrown upward by centrifugal force from therotation of the second gear 152, passing through the opening 156 so asto be supplied to the oil reservoir 164. In the exemplary embodimentshown in FIG. 28, as well, the lubricating oil is transferred to the oilreservoir 164 in two steps, the first being the transfer of thelubricating oil by rotation of the first gear 153, and the second beingthe transfer of the lubricating oil by rotation of the second gear 152.Accordingly, even if the first gear 153 is separated from the oilreservoir 164, a reduction in the amount of lubricating oil supplied tothe oil reservoir 164 is able to be suppressed.

Also, because the lubricating oil is retained by the tooth grooves ofthe second gear 152, the lubricating oil retaining function of thesecond gear 152 is improved. Further, the recessed portion 162 isprovided that temporarily retains the lubricating oil in the transferprocess between the first gear 153 and the second gear 152. Accordingly,the lubricating oil is able to be transferred reliably between the firstgear 153 and the second gear 152. Further, because the lubricating oilis pushed out from between the first gear 153 and the second gear 152,the ability of the lubricating oil to separate from the first gear 153is improved. Furthermore, it is possible to suppress an increase in thesurface area of the first gear 153 that is submersed in the lubricatingoil sump A1. As a result, it is also possible to suppress an increase inpower loss of the second rotating shaft 157.

Sixteenth Embodiment

A sixteenth exemplary embodiment is shown in FIG. 32. The structuresshown in FIG. 32 that are the same as those in FIGS. 18 and 20 shall bedenoted by the same reference numerals as in FIGS. 18 and 20, anddescriptions thereof will be omitted. That is, the guide member 122 isprovided to the side of the side face 123 of the first gear 107. One endportion of the guide member 122 is provided along the side of the secondgear 108. The teeth formed on the outer periphery of the second gear 108have a so-called trapezoidal shape, with teeth grooves formed betweenadjacent teeth. The guide member 121, which is continuous from the oilreservoir 105, is formed above the second gear 108.

In FIG. 32, the directions of rotation of the first gear 107, the secondgear 108, and the third gear 124 are the same as in FIG. 20. Also inFIG. 32, the lubricating oil in the lubricating oil sump A1 istransferred to the top face of the guide member 122, just as in FIG. 20.This lubricating oil runs into the tooth grooves of the second gear 108,after which it is thrown upward onto the top face of the guide member121 by centrifugal force from the rotation of the second gear 108. Thelubricating oil that has been thrown upward onto the top face of theguide member 121 then runs into the oil reservoir 105, just as in FIG.18. The component parts in the exemplary embodiment shown in FIG. 18that are the same as those in the exemplary embodiments shown in FIGS.18 and 20 provide the same operation and effects obtained in theexemplary embodiments shown in FIGS. 18 and 20.

Also, in the exemplary embodiment shown in FIG. 32, there is nostructure corresponding to the lubricating oil sump C1 in which thesecond gear 108 is submersed, nor is there a retaining portion forforming the lubricating oil sump. That is, the lubricating oil that runsalong the guide member 122 runs directly into the tooth grooves of thesecond gear 108. The teeth on the second gear 108 have a trapezoidalshape and are few in number so the volumetric capacity of the toothgrooves is expanded. Accordingly, the amount of lubricating oil retainedis able to be increased, such that the amount of lubricating oilsupplied to the oil reservoir 105 is increased. Also, the number ofparts that do not have a retaining portion are reduced. In the otherexemplary embodiments beside that shown in FIG. 32, as well, the teethof the gears can also be made to have a trapezoidal shape. Further, ineach of the foregoing exemplary embodiments, the curve of the toothprofile of the gears may be an involute curve or a cycloid curve or thelike.

The foregoing exemplary embodiment may be applied to a powertransmission device arranged between a driving force source (not shown)and wheels (also not shown) of a vehicle. When this type of powertransmission device for a vehicle is mounted in a vehicle, the powertransmission device may be arranged within a casing. More specifically,an engine is provided as the driving force source and the casing ismounted to the outer wall of the engine. An electric motor and agenerator that function as other driving force sources are arrangedwithin this casing.

A power combining mechanism, a transmission, and differential gears areexamples of power transmission devices that can be housed within thecasing. Power from the engine and the electric motor may be transmittedto the transmission via the power combining mechanism. That is, theforegoing exemplary embodiments can be applied to a power train of avehicle that is a type of a hybrid vehicle, i.e., to a vehicle havingboth an engine and an electric motor. Also, the lubrication systemsdescribed in the foregoing embodiments are arranged within the casingand provide lubricating oil to parts requiring lubrication without theuse of an oil pump.

Further, in the exemplary embodiments described above, lubricating oilis supplied to the oil reservoir. Alternatively, however, lubricatingoil can also be supplied to parts requiring lubrication, such as gearbearings, gear meshing portions, and reservoirs and the like.

In above embodiments, although a portion to which the lubricating oilsupplied is referred to as the oil reservoir, the portion may bereferred to as a reservoir portion or a catch tank.

1. A planetary gearset comprising: a rotating element which is oneelement from among a sun gear, a ring gear, and a carrier that rotatablyretains a plurality of pinion gears arranged between the sun gear andthe ring gear, and which transmits torque between said rotating elementand an external member provided eccentric with respect to said rotatingelement; a fixed element which is one element from among the sun gear,the ring gear, and the carrier, said fixed element being an elementother than the rotating element, which is retained so as to be able tomove without rotation in a predetermined radial direction of a load fromthe transmission of torque between the rotating element and the externalmember, and which is constructed such that the load from thetransmission of torque between the rotating element and the externalmember is received by a fixed portion that rotatably retains thatrotating element; and a permanent gap between said rotating element anda bearing therefore.
 2. A planetary gearset according to claim 1,wherein said fixed element is retained by coupling means in a form of agrooved spline such that said fixed element is allowed to move withoutrotation in said predetermined radial direction parallelly to said load,and wherein this radial movement is allowed to such extent that saidload is received through a reaction force of a same size as the load bysaid fixed portion.
 3. The planetary gearset of claim 1, furthercomprising a permanent gap adjacent to said rotating element configuredto allow the rotating element to rotate.
 4. The planetary gearset ofclaim 1, further comprising a grooved spline provided between said fixedelement and a casing configured to allow the fixed element to movewithout rotation in said predetermined radial direction.
 5. Theplanetary gearset of claim 1, wherein the fixed element is retained onsaid fixed portion by an elastic member.
 6. A planetary gearsetcomprising: a rotating element which is one element from among a sungear, a ring gear, and a carrier that rotatably retains a plurality ofpinion gears arranged between the sun gear and the ring gear, and whichtransmits torque between said rotating element and an external memberprovided eccentric with respect to said rotating element; and a fixedelement which is one element from among the sun gear, the ring gear, andthe carrier, said fixed element being an element other than the rotatingelement, which is retained so as to be able to move without rotation ina predetermined radial direction of a load from the transmission oftorque between the rotating element and the external member, and whichis constructed such that the load from the transmission of torquebetween the rotating element and the external member is received by afixed portion that rotatably retains that rotating element, wherein thefixed element is the carrier and the rotating element is the ring gear.7. A planetary gearset comprising: a rotating element which is oneelement from among a sun gear, a ring gear, and a carrier that rotatablyretains a plurality of pinion gears arranged between the sun gear andthe ring gear, and which transmits torque between said rotating elementand an external member provided eccentric with respect to said rotatingelement; and a fixed element which is one element from among the sungear, the ring gear, and the carrier, said fixed element being anelement other than the rotating element, which is retained so as to beable to move without rotation in a predetermined radial direction of aload from the transmission of torque between the rotating element andthe external member, and which is constructed such that the load fromthe transmission of torque between the rotating element and the externalmember is received by a fixed portion that rotatably retains thatrotating element, wherein said external member is a counter gear, saidrotating element is the ring gear, and said ring gear is meshed withpinion gears.
 8. The planetary gearset of claim 7, wherein externalteeth of said ring gear are meshed with said counter gear.
 9. Theplanetary gearset according to claim 6, further comprising: a pluralityof pinion pins rotatably retained on the pinion gears by bearings, thepinion pins being fixed to the carrier; an oil path configured toconnect axial ends of the pinion pins from an axial end of the pinionpin on an upper level side to the axial end of the pinion pin on a lowerlevel side in that order, the oil path formed on the axial end side ofthe pinion pins so as to lead lubricating oil that runs down from above;and an oil sump formed in a location corresponding to the axial end ofat least one of the pinion pins and into which the lubricating oil thatruns down the oil path runs, the oil sump collecting the lubricatingoil, and being intercommunicated with the bearing of the at least one ofthe pinion pins.
 10. The planetary gearset according to claim 6, furthercomprising: a plurality of pinion pins rotatably retained on the piniongears by bearings, the pinion pins being fixed to the carrier; aplurality of oil holes extending from axial ends of the pinion pins tothe bearings; an oil path configured to connect open ends of the oilholes from the open end of the oil hole on an upper side to an open endof the oil hole on a lower side in that order, the oil path being formedon an axial end side to which the oil holes of the pinion pins open soas to lead lubricating oil that runs down from above; and an oil sumpformed in a location corresponding to the open end of at least one ofthe oil holes, into which the lubricating oil that runs down the oilpath runs, the oil sump collecting the lubricating oil, and beingintercommunicated with the at least one of the oil holes.
 11. Theplanetary gearset according to claim 9, further comprising: a firstrotating body configured to transfer the lubricating oil by rotating;and a second rotating body configured to retain the lubricating oiltransferred by the first rotating body and to transfer, by rotating, thelubricating oil to a portion requiring lubrication provided at an upperlevel end of the oil path.
 12. The planetary gearset according to claim11, wherein the second rotating body has formed therein a recessedportion that retains the lubricating oil.
 13. The planetary gearsetaccording to claim 11, further comprising: a transfer portion configuredto temporarily retain the lubricating oil in at least one of a path thattransfers the lubricating oil from the first rotating body to the secondrotating body and a path that transfers the lubricating oil from thesecond rotating body to a portion requiring lubrication.
 14. Theplanetary gearset according to claim 13, wherein the transfer portion isa portion that picks up the lubricating oil adhered to at least one endface of one of the first rotating body and the second rotating body. 15.The planetary gearset according to claim 13, further comprising: apushing out mechanism configured to push the lubricating oil retained inat least one of the first rotating body and the second rotating body outin an axial direction of the rotating body, and to lead the lubricatingoil to at least one path from among the path that transfers thelubricating oil from the first rotating body to the second rotating bodyand the path that transfers the lubricating oil from the second rotatingbody to a portion requiring lubrication.
 16. The planetary gearsetaccording to claim 11, wherein an upper level edge of the portionrequiring lubricating is higher than an upper edge of the first rotatingbody.
 17. The planetary gearset according to claim 11, wherein arotation speed of the second rotating body is faster than a rotationspeed of the first rotating body.
 18. The planetary gearset according toclaim 11, wherein: the sun gear, the ring gear, and the pinion gears arerotating members for transmitting power between a driving force sourceand a wheel; and the first rotating body is coupled with one of the sungear and the ring gear and is submersed in a main lubricating oil sump.19. The planetary gearset according to claim 1, further comprising: afirst rotating body configured to transfer lubricating oil by rotating;and a second rotating body configured to retain the lubricating oiltransferred by the first rotating body and to transfer, by rotating, thelubricating oil to a portion requiring lubrication provided at an upperend of the rotating element.